EP2992158B1 - Improvements in damper assemblies - Google Patents
Improvements in damper assemblies Download PDFInfo
- Publication number
- EP2992158B1 EP2992158B1 EP14720584.3A EP14720584A EP2992158B1 EP 2992158 B1 EP2992158 B1 EP 2992158B1 EP 14720584 A EP14720584 A EP 14720584A EP 2992158 B1 EP2992158 B1 EP 2992158B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pin
- cylinder
- damper
- piston assembly
- assembly
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000000712 assembly Effects 0.000 title description 6
- 238000000429 assembly Methods 0.000 title description 6
- 239000012530 fluid Substances 0.000 claims description 25
- 238000013016 damping Methods 0.000 claims description 16
- 230000000694 effects Effects 0.000 claims description 3
- 229920003023 plastic Polymers 0.000 description 5
- 239000004033 plastic Substances 0.000 description 5
- 238000004891 communication Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 230000037361 pathway Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 239000007787 solid Substances 0.000 description 2
- 230000008867 communication pathway Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/52—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics in case of change of temperature
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
- E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
- E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
- E05F3/12—Special devices controlling the circulation of the liquid, e.g. valve arrangement
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
- E05F5/00—Braking devices, e.g. checks; Stops; Buffers
- E05F5/06—Buffers or stops limiting opening of swinging wings, e.g. floor or wall stops
- E05F5/10—Buffers or stops limiting opening of swinging wings, e.g. floor or wall stops with piston brakes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/342—Throttling passages operating with metering pins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/368—Sealings in pistons
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
- E05Y2900/00—Application of doors, windows, wings or fittings thereof
- E05Y2900/20—Application of doors, windows, wings or fittings thereof for furniture, e.g. cabinets
Definitions
- the piston rod 11 extends into the cylinder 10 through a hole in an end cap 12 and is surrounded by a seal 13.
- the end cap 12 is fixed to the cylinder 10 and seals off its open end, thus creating an enclosed inner space within the cylinder.
- the inner space contains a damping fluid such as oil.
- the piston 14 comprises outer and inner flanges 14a, 14b.
- the outer diameter of the flanges 14a, 14b is slightly less than the bore of the cylinder 10. This means that the piston assembly 14 is able to move freely within the cylinder 10 along its longitudinal axis. It also means that there is a small gap between the flanges 14a, 14b and the cylinder 10, which constitutes a pathway for the passage of damping fluid between the chambers.
- the amount of leakage of fluid by this means is arranged to decrease over the working stroke of the piston assembly 14, due to the tapering form of the channels 21. Accordingly, the main factor that determines the magnitude of the damping force that the assembly will exert on its working stroke is the size of the gap between the hole 17 and the pin 30 located within it.
- the piston assembly 14 is seen in greater detail in Figure 2 . It will be seen that the hole 17 has a reduced diameter section which produces a shoulder 31 at the inner end of the piston assembly 14. The effect of this is to capture the elongate pin 30 in the hole 17 between the shoulder 31 and the inner end of the piston rod 11. The length of the pin 30 is somewhat less than the extent of the hole 17 between the shoulder 31 and the inner end of the piston rod 11. This means that the pin 30 is able to move axially within the hole 17 between end positions.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Description
- This invention relates to damper assemblies and in particular, though not exclusively, to damper assemblies for cushioning movement of furniture parts such as doors or drawers.
-
- According to the present invention there is provided a damper assembly comprising a cylinder with a piston assembly which is mounted for reciprocal movement therein and which divides the cylinder into separate chambers with a restricted flow path therebetween for passage of damping fluid contained within the cylinder. The restricted flow path is defined between elements whose shape and/or relative position is designed to vary with temperature. The elements are arranged so that the effective size of the restricted flow path therebetween reduces as temperature increases. One of the elements is an elongate pin. The pin is located within a hole of the piston assembly having a cross-sectional shape whose area varies with respect to a longitudinal axis of the cylinder.
- By way of example, embodiments of the invention will now be described with reference to the accompanying drawings, in which:
-
Figure 1 is a cross-sectional view of a damper assembly according to the invention, -
Figures 2, 3 and 4 are cross-sectional views of the piston assembly of theFigure 1 assembly in various different conditions, -
Figure 5 is a detail from the piston assembly ofFigure 1 , -
Figures 6 and 7 are cross-sectional views of other forms of piston assembly for the damper assembly ofFigure 1 , and -
Figures 8 and 9 are details from the piston assemblies ofFigures 6 and 7 respectively. - The damper assembly seen in
Figure 1 comprises anelongate cylinder 10 which is closed at one end, and apiston rod 11 arranged for reciprocal movement along the longitudinal axis of the cylinder. Thepiston rod 11 is conveniently formed from plain rod stock of circular cross-section. Thecylinder 10 is conveniently of plastics. - The
piston rod 11 extends into thecylinder 10 through a hole in anend cap 12 and is surrounded by aseal 13. Theend cap 12 is fixed to thecylinder 10 and seals off its open end, thus creating an enclosed inner space within the cylinder. The inner space contains a damping fluid such as oil. - At its inner end, the
piston rod 11 is designed to engage apiston assembly 14. Thepiston assembly 14 is conveniently made of plastics and effectively divides the inner space within thecylinder 10 into separate chambers. Acompression spring 15 arranged in one of the chambers between the closed end of thecylinder 10 and thepiston assembly 14 acts to bias thepiston rod 11 towards its extended position (seen inFigure 1 ). - The
piston 14 comprises outer andinner flanges 14a, 14b. The outer diameter of theflanges 14a, 14b is slightly less than the bore of thecylinder 10. This means that thepiston assembly 14 is able to move freely within thecylinder 10 along its longitudinal axis. It also means that there is a small gap between theflanges 14a, 14b and thecylinder 10, which constitutes a pathway for the passage of damping fluid between the chambers. - The
flanges 14a, 14b are spaced apart axially and in the space between them is located a seal 16, preferably in the form of an O-ring. The seal 16 is in sealing engagement with the bore of thecylinder 10, but not with thepiston assembly 14. - The
piston assembly 14 has ahole 17 therethrough, to allow a fluid communication pathway between the chambers. Anelongate pin 30 is located within thehole 17. This arrangement provides a controlled restricted flow path for passage of damping fluid across the piston assembly, as is described in greater detail below. - On the
outer flange 14a of thepiston 14, thehole 17 has a counterbore 18. As will be seen, the counterbore 18 is designed to receive an inner end section 11a of thepiston rod 11. The inner end section 11a is arranged to be received in the counterbore 18 with an interference fit. This arrangement means that the piston assembly is able to provide lateral support for the piston rod at its inner end in its reciprocal movement within thecylinder 10. - The counterbore 18 is provided with one or more axially extending grooves (not shown) on its inner surface. The purpose of these grooves is to provide communication across the
piston assembly 14 to allow passage of damping fluid between the chambers. The passageway provided by this means is designed to be greater than the restricted flow path defined between thepin 30 andhole 17, to ensure that this latter will act as the damping control mechanism. - A collar 19 is seen on the
piston rod 11 towards its inner end. The collar 19 is preferably of metal and is formed on or attached to thepiston rod 11 by suitable means such as stamping or moulding. The purpose of the collar 19 is to spread the load on thepiston assembly 14 when a force, e.g. from a closing door, acts on thepiston rod 11. This is an important consideration, because the fluid pressures that occur in damper assemblies of this nature can be quite substantial and plastics components can distort and break or jam in the cylinder if they are not adequately supported. - The collar 19 is designed to engage the axial end face of the
outer flange 14a with its annular surface. The cross-sectional area of the annular surface of the collar 19 is at least twice as big as the cross-sectional area of thepiston rod 11, and preferably four or five times as big. - A resiliently
collapsible element 20 of known design is contained within one of the chambers. The purpose of thiselement 20 is to compensate for changes in volume in thecylinder 10 that result from movements of thepiston assembly 14. - The
cylinder 10 has a number ofrelief channels 21 extending axially in the surface of its bore. Thechannels 21 are arranged to taper in depth towards the closed end of thecylinder 10, i.e. their depth decreases progressively in this direction. The purpose of thesechannels 21 is to allow a progressively variable amount of fluid communication between the chambers as thepiston assembly 14 moves axially within thecylinder 10 and hence produce a progressive variation in the damping resistance provided by the assembly. - In operation, the assembly will normally be in the position seen in
Figure 1 , with itspiston rod 11 fully extended from thecylinder 10. When the distal end of thepiston rod 11 is struck, e.g. by a closing door, this will cause thepiston rod 11 to force thepiston assembly 14 towards the closed end of thecylinder 10, against the bias of thespring 15. At the same time, theouter flange 14a of thepiston 14 will move into engagement with the seal 16, thus closing off the fluid pathway between the outer flange and thecylinder 10. Mainly, therefore, fluid moving across thepiston assembly 14 from one chamber to the other has to pass through thehole 17. A certain amount of fluid is also able to leak between the two chambers via therelief channels 21. However, the amount of leakage of fluid by this means is arranged to decrease over the working stroke of thepiston assembly 14, due to the tapering form of thechannels 21. Accordingly, the main factor that determines the magnitude of the damping force that the assembly will exert on its working stroke is the size of the gap between thehole 17 and thepin 30 located within it. - When the force on the distal end of the
piston rod 11 has dissipated, the piston rod will be returned to its extended position by the biasing force of thespring 15 acting on thepiston 14. This movement moves the seal 16 from its engagement with theouter flange 14a of thepiston 14 into engagement with the inner flange 14b. In this position, a far greater degree of fluid communication is opened up between the two chambers. This greatly eases the flow of damping fluid across thepiston 14 and thus means that on the return movement of thepiston rod 11, there is little effective damping resistance. - The
piston assembly 14 is seen in greater detail inFigure 2 . It will be seen that thehole 17 has a reduced diameter section which produces ashoulder 31 at the inner end of thepiston assembly 14. The effect of this is to capture theelongate pin 30 in thehole 17 between theshoulder 31 and the inner end of thepiston rod 11. The length of thepin 30 is somewhat less than the extent of thehole 17 between theshoulder 31 and the inner end of thepiston rod 11. This means that thepin 30 is able to move axially within thehole 17 between end positions. - It will also be seen that the
hole 17 is not cylindrical, but tapering towards the inner end of thepiston assembly 14. This means that thepin 30 is effectively located within an openended conical chamber. The end of thepin 30 within the conical chamber defined by thehole 17 can be seen inFigure 5 . -
Figure 2 shows the condition of thepiston assembly 14 after thespring 15 has returned thepiston rod 11 to its normally extended position. In this condition, thepin 30 is in its innermost axial end position, located on theshoulder 31 of thehole 17. In this position, the gap between thepin 30 and thehole 17 is at is smallest. It will also be noted that the seal 16 in this condition of thepiston assembly 14 is located on the inner flange 14b. -
Figure 3 shows the condition of thepiston assembly 14 when thepiston rod 11 experiences an impact, e.g. from a closing door. Thepiston rod 11 forces thepiston assembly 14 further into thecylinder 10 against the biasing action of thespring 15. As thepiston assembly 14 moves, it picks up the seal 16, which is in sealing engagement with the bore of thecylinder 10. The seal 16 is now in sealing engagement with theouter flange 14a, thus effectively closing off fluid communication around the outside of the piston assembly 14 (other than via the relief channels, which are not shown here). Inward movement of thepiston rod 11 thus sets up a pressure differential across thepiston assembly 14, effectively forcing fluid through thehole 17. This flow of fluid causes thepin 30 to move axially in thehole 17 to its opposite end position, abutting against the inner end of thepiston rod 11. - The amount of fluid that is able to flow through the
hole 17 is governed by the gap between it and thepin 30. As will be understood fromFigure 5 , this depends upon the diameter of thepin 30 and the axial position of its inner end along the tapering shape of thehole 17. The position of the inner end of thepin 30 when it is in abutting engagement with the inner end of thepiston rod 11 is determined by its length. Depending upon the design of thepin 30, however, and in particular, the material of which it is made, its length will vary with temperature, according to its coefficient of thermal expansion. As the temperature of thepin 30 increases, so its length will increase (and also to some extent its diameter, but less significantly). This phenomenon can be used to provide compensation for temperature changes in the damper assembly. - In use, damper assemblies of this nature can become heated, due to the action of the damping fluid being forced through restricted passageways. Typically, the viscosity of damping fluids tends to decrease as their temperature increases. Accordingly, a rise in temperature in such a damping assembly will tend to result in a decrease in the amount of damping that it is able to generate. The arrangement seen here is able to compensate for such temperature changes.
- As will be seen, an increase in the length of the
pin 30 due to a rise in temperature will mean that its inner end is nearer the inner end of thehole 17, i.e. further down its taper. This is the condition seen inFigure 4 , which contrasts with the condition seen inFigure 3 . The net effect is that the gap between thepin 30 and thehole 17 is smaller. This gap constitutes the restricted passageway that effectively controls the flow of fluid across thepiston assembly 14. The arrangement means, therefore, that as the temperature of the assembly, and hence thepin 30, rises, the pin will expand and thus the effective gap between it and thehole 17 will be reduced. The loss of viscosity in the damping fluid due to its rise in temperature is thus compensated for by the fact that it must now pass through a more restricted passageway. - In the example shown in
Figures 1 to 5 , thepin 30 is in the form of a solid rod of circular cylindrical shape and is of a material, typically plastics, with a suitable coefficient of thermal expansion. It will be understood, however, that many different alternative arrangements are possible. For example, the pin could be made as a thin-walled component, rather than being solid; it could be formed of bi-metal or other material to give a suitable expandability; it could be arranged to expand laterally as well as or instead of axially; or it could itself to made as a conical element. Also the hole in which the pin is located could be designed in different ways. For example, instead of being conical in shape, it could be formed as a cylindrical hole and be provided with axially extending grooves of variable depth, akin to the tapering relief channels in the cylinder described above. - An alternative design of
piston assembly 114 is seen inFigure 6 . Here, thepiston assembly 114 has an axially extending bore therethrough in the form of a plaincylindrical hole 117. Located within and freely movable in thishole 117 is aneolngate pin 130. Thepin 130 has a plaincylindrical shank 131 and alarger diameter head 132, with aconical taper 133 in the transition therebetween. Thepiston assembly 114 has acounterbore 134 at its inner end, arranged co-axially with thehole 117 and thus defining ashoulder 135. Thecounterbore 134 is sized to receive thehead 132 of thepin 130 andprojection 136 retains it in position. - The
pin 130 is configured so that when its other end is in abutting engagement with the inner end 11a of thepiston rod 11, itstaper 133 will be in close proximity to theshoulder 135, as will be seen inFigure 8 . The gap therebetween determines the effective size of the fluid flow path across thepiston assembly 114. In this case, thepin 130 is designed to have a lower coefficient of thermal expansion than thepiston assembly 114, conveniently by making the pin of metal and the piston assembly of plastics. Now, if there should be a rise in temperature, eg due to the damper assembly being subjected to a heavy workload, this will result in a proportionately greater axial elongation of thepiston assembly 114 than of thepin 130. This will effectively cause the position of theshoulder 135 to move nearer relative to thetaper 133, resulting in a diminution of the size of the flow path therebetween. The arrangement is thus able to provide the same effective temperature-dependent compensation as with the previously described example. - The alternative form of
piston assembly 214 seen inFigure 7 is designed to operate in much the same way as theFigure 6 assembly, with apin 230 being located in ahole 217 with acounterbore 234 defining a shoulder 235, and with the pin having a lower coefficient of thermal expansion than the piston assembly. The restricted flow path across the piston assembly here is again defined by the gap between the shoulder 235 and the head of thepin 230, but here the pin has a basicallyflat head 231. Changes in temperature here will again cause differential expansion of the pin and piston assembly, thus effectively altering the gap between thehead 231 of thepin 230 and the shoulder 235 and hence the size of the fluid pathway across the piston assembly.
Claims (9)
- A damper assembly comprising a cylinder (10) with a piston assembly (14) which is mounted for reciprocal movement therein and which divides the cylinder (10) into separate chambers with a restricted flow path therebetween for passage of damping fluid contained within the cylinder (10), wherein the restricted flow path is defined between elements whose shape and/or relative position is designed to vary with temperature;
wherein the elements are arranged so that the effective size of the restricted flow path therebetween reduces as temperature increases;
wherein one of the elements is an elongate pin (30);
wherein the pin (30) is located within a hole (17) of the piston assembly (14) having a cross-sectional shape whose area varies with respect to a longitudinal axis of the cylinder (10);
characterized in that the pin (30) is arranged to be movably axially within said hole (17) of the piston assembly (14). - A damper assembly as claimed in claim 1 wherein said variation of the restricted flow path is caused by the effects of thermal expansion in the direction of the longitudinal axis of the cylinder (10).
- A damper assembly as claimed in claim 1 or claim 2 wherein the pin (30) is arranged with its longitudinal axis parallel to the longitudinal axis of the cylinder (10).
- A damper assembly as claimed in any one of claims 1 to 3 wherein the hole (17) of the piston assembly (14) is conical in shape.
- A damper as claimed in any one of claims 1 to 3 wherein the hole (17) of the piston assembly (14) is essentially cylindrical in shape but includes a shoulder.
- A damper as claimed in any one of claims 1 to 5 wherein the cross-sectional shape of the pin (30) varies with respect to its longitudinal axis.
- A damper as claimed in claim 6 wherein at least part of the pin (30) is conical in shape.
- A damper as claimed in claim 5, claim 6 or claim 7 wherein the pin (30) has an enlarged head (133).
- A damper as claimed in claim 8 wherein the head (133) of the pin (30) is conical.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB1308054.4A GB2513848A (en) | 2013-05-03 | 2013-05-03 | Improvements in damper assemblies |
PCT/EP2014/058619 WO2014177521A1 (en) | 2013-05-03 | 2014-04-28 | Improvements in damper assemblies |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2992158A1 EP2992158A1 (en) | 2016-03-09 |
EP2992158B1 true EP2992158B1 (en) | 2020-09-16 |
Family
ID=48627292
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14720584.3A Active EP2992158B1 (en) | 2013-05-03 | 2014-04-28 | Improvements in damper assemblies |
Country Status (5)
Country | Link |
---|---|
US (1) | US10280999B2 (en) |
EP (1) | EP2992158B1 (en) |
CN (1) | CN105308251B (en) |
GB (1) | GB2513848A (en) |
WO (1) | WO2014177521A1 (en) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105179557B (en) * | 2015-10-23 | 2018-09-14 | 广东美的厨房电器制造有限公司 | Hydraulic damper and hinge |
CN105299126B (en) * | 2015-11-21 | 2017-12-05 | 平顶山学院 | A kind of two-stage buffer with temperature-detecting device |
DE102015015170B3 (en) * | 2015-11-26 | 2016-12-15 | Günther Zimmer | Cylinder-piston unit with compensating sealing element |
US10145162B2 (en) * | 2016-03-02 | 2018-12-04 | King Slide Works Co., Ltd. | Damping device and furniture hinge comprising the same |
DE102017102078A1 (en) * | 2017-02-02 | 2018-08-02 | Druck- und Spritzgußwerk Hettich GmbH & Co. KG | Brake device and furniture or household appliance with a braking device |
ES2818614T3 (en) * | 2017-07-24 | 2021-04-13 | Auxiliares Ind | Compensating double sealing gasket for hydraulic shock absorbers applicable in self-closing furniture |
CN107419985A (en) * | 2017-09-13 | 2017-12-01 | 厦门德浦精密科技有限公司 | A kind of damper with temperature-compensating |
US10961673B2 (en) * | 2017-12-04 | 2021-03-30 | Abbas Nejati | Retractable speed bump and a method for retracting a speed bump |
GB201801231D0 (en) * | 2018-01-25 | 2018-03-14 | Titus D O O Dekani | Improvements in dampers |
US11590639B2 (en) * | 2018-03-01 | 2023-02-28 | Max Co., Ltd. | Fluid damper and driving tool |
EP3760895A4 (en) * | 2018-03-01 | 2021-12-08 | Max Co., Ltd. | Fluid damper and driving tool |
US11739808B2 (en) * | 2018-03-28 | 2023-08-29 | Piolax, Inc. | Damper |
US11920401B2 (en) | 2021-05-03 | 2024-03-05 | Kohler Co. | Slow close mechanism for sliding applications |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2909248A (en) * | 1957-04-12 | 1959-10-20 | Houdaille Industries Inc | Linear damper |
US3483585A (en) * | 1966-11-12 | 1969-12-16 | Ver Baubeschlag Gretsch Co | Door closer with means for damping the closing movement of the door |
US20110056781A1 (en) * | 2009-09-10 | 2011-03-10 | Kayaba Industry Co., Ltd. | Fluid pressure shock absorber |
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US3577157A (en) * | 1965-10-22 | 1971-05-04 | Foxboro Co | Integrating device for use in industrial process control apparatus |
DE1584236A1 (en) * | 1966-11-12 | 1970-07-30 | Ver Baubeschlag Gretsch Co | Door closer |
FR1587512A (en) * | 1967-11-04 | 1970-03-20 | ||
US3791494A (en) * | 1971-03-11 | 1974-02-12 | Maremont Corp | Temperature compensating means for a hydraulic shock absorber |
DE2340987A1 (en) * | 1973-08-14 | 1975-02-27 | Bilstein August Fa | SHOCK ABSORBER VALVE, IN PARTICULAR ITEM EQUIPPED WITH IT, FOR HYDROPNEUMATIC MOTOR VEHICLE SINGLE PIPE DAMPERS |
US4148111A (en) * | 1977-11-30 | 1979-04-10 | Reading Door Closer Corp. | Temperature compensating hydraulic door closer |
DE3328347A1 (en) * | 1983-08-05 | 1985-02-14 | Fichtel & Sachs Ag, 8720 Schweinfurt | VIBRATION DAMPER OR SHOCK ABSORBER WITH TEMPERATURE COMPENSATION |
GB2156950B (en) * | 1984-04-04 | 1988-01-13 | Newman Tonks Eng | Flow control valve and door closer incorporating such a valve |
JPS62155346A (en) * | 1985-12-27 | 1987-07-10 | Toyota Motor Corp | Valve structure of hydraulic buffer |
FR2594510B1 (en) * | 1986-02-18 | 1988-06-24 | Bourcier Carbon Christian | HYDRAULIC SHOCK ABSORBER WITH CONTROLLED DAMPING |
WO1991003664A1 (en) * | 1989-09-11 | 1991-03-21 | Stabilus Gmbh | Self-blocking gas spring with temperature-responsive bypass valve |
US4973024A (en) * | 1989-09-26 | 1990-11-27 | Toki Corporation Kabushiki Kaisha | Valve driven by shape memory alloy |
US5967268A (en) * | 1997-03-17 | 1999-10-19 | Tenneco Automotive Inc. | Temperature responsive damper |
DE10228510B4 (en) * | 2002-06-26 | 2013-09-12 | Geze Gmbh | Valve for a door closer |
US6974001B2 (en) * | 2003-11-19 | 2005-12-13 | Arvinmeritor Technology, Llc. | Temperature compensating gas spring |
DE102005004982B4 (en) * | 2005-02-04 | 2013-03-21 | Stabilus Gmbh | gas spring |
US9371883B2 (en) * | 2011-07-28 | 2016-06-21 | Robert H. Wehr | Inertial terrain transit event manager apparatus |
GB2498747B (en) * | 2012-01-24 | 2018-05-09 | Titus Int Ltd | Improvements in damper assemblies |
GB201207304D0 (en) * | 2012-04-25 | 2012-06-06 | Titus Internat Ltd | Improvements in dampers |
-
2013
- 2013-05-03 GB GB1308054.4A patent/GB2513848A/en not_active Withdrawn
-
2014
- 2014-04-28 WO PCT/EP2014/058619 patent/WO2014177521A1/en active Application Filing
- 2014-04-28 US US14/888,805 patent/US10280999B2/en active Active
- 2014-04-28 CN CN201480034074.5A patent/CN105308251B/en not_active Expired - Fee Related
- 2014-04-28 EP EP14720584.3A patent/EP2992158B1/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2909248A (en) * | 1957-04-12 | 1959-10-20 | Houdaille Industries Inc | Linear damper |
US3483585A (en) * | 1966-11-12 | 1969-12-16 | Ver Baubeschlag Gretsch Co | Door closer with means for damping the closing movement of the door |
US20110056781A1 (en) * | 2009-09-10 | 2011-03-10 | Kayaba Industry Co., Ltd. | Fluid pressure shock absorber |
Also Published As
Publication number | Publication date |
---|---|
CN105308251A (en) | 2016-02-03 |
CN105308251B (en) | 2017-09-12 |
US20160076618A1 (en) | 2016-03-17 |
EP2992158A1 (en) | 2016-03-09 |
WO2014177521A1 (en) | 2014-11-06 |
GB2513848A (en) | 2014-11-12 |
US10280999B2 (en) | 2019-05-07 |
GB201308054D0 (en) | 2013-06-12 |
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